WO2020252854A1 - 具有矢量摆线变速机构的可变气门正时装置 - Google Patents

具有矢量摆线变速机构的可变气门正时装置 Download PDF

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Publication number
WO2020252854A1
WO2020252854A1 PCT/CN2019/098610 CN2019098610W WO2020252854A1 WO 2020252854 A1 WO2020252854 A1 WO 2020252854A1 CN 2019098610 W CN2019098610 W CN 2019098610W WO 2020252854 A1 WO2020252854 A1 WO 2020252854A1
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WO
WIPO (PCT)
Prior art keywords
sprocket
camshaft
ball
cycloidal
output part
Prior art date
Application number
PCT/CN2019/098610
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English (en)
French (fr)
Inventor
陈飞龙
马武坤
欧日燊
李林锋
Original Assignee
海尚集团有限公司
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Filing date
Publication date
Application filed by 海尚集团有限公司 filed Critical 海尚集团有限公司
Publication of WO2020252854A1 publication Critical patent/WO2020252854A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/352—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using bevel or epicyclic gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/032—Electric motors

Definitions

  • the present invention relates to the technical field of changing the opening and closing timing of the intake and exhaust valves of an engine.
  • the intake valve for supplying the fuel mixture to the engine and the exhaust valve for discharging the combustion gas have been opened and closed according to the operating stroke of the engine.
  • a variable valve timing device having a vector cycloid transmission mechanism that changes the opening and closing timing of these valves in accordance with the operating conditions of the engine.
  • variable valve timing device for example, as shown in FIGS. 9 and 10, there is a variable valve timing device that connects a camshaft 41 that drives a valve of an engine to a camshaft 41 that transmits rotation from the engine and drives the camshaft 41 to rotate.
  • the sprocket 42 is relatively rotatably arranged coaxially, and the rotation of the output shaft 44 of the electric motor 43 arranged coaxially with the camshaft 41 is transmitted to the camshaft 41 via the reduction mechanism 45 and the link mechanism 46, so that The camshaft 41 rotates relative to the sprocket 42 to change the rotational phase difference between the two, thereby changing the opening and closing timing of the valve.
  • the reduction mechanism 45 is configured such that a part of the teeth of the internal gear 47 meshes with the external gear 49 provided in the housing 48 integrated with the sprocket 42.
  • the internal gear 47 is rotatably supported by the electric motor by bearings.
  • the eccentric shaft portion 44a of the output shaft 44 of 43 so that when the output shaft "relatively rotates with respect to the sprocket 42, the internal gear 47 rotates around the eccentric shaft portion 44a, and the reduction mechanism 45 rotates the internal gear 47
  • the rotation of the guide plate 50 is transmitted to the guide plate 50, and the rotation of the guide plate 50 is further transmitted to the cam plate 41a that rotates integrally with the camshaft 41 via the link mechanism 46 composed of arms 46a and 46b, so that the camshaft 41 rotates relative to the sprocket 42.
  • the rotation phase of the camshaft 41 with respect to the rotation phase of the crankshaft can be changed, thereby changing the timing of opening and closing the intake valve or exhaust valve of the engine.
  • the electric variable valve timing device described above is a mechanism that transmits the rotation of the output shaft 44 of the electric motor 43 to the camshaft 41, and forms a complicated structure combining the reduction mechanism 45 and the link mechanism 46, which cannot be compact. The problem of designing the device carefully.
  • the RV reducer is used between the sprocket and the camshaft to achieve the rotational phase difference between the camshaft and the sprocket.
  • the present invention provides a variable valve timing device with a vector cycloid transmission mechanism with few parts and a small volume.
  • a variable valve timing device with a vector cycloid transmission mechanism including a camshaft that drives the intake valve or exhaust valve of the engine, and rotates coaxially with the camshaft
  • the sprocket and the motor that changes the rotation phase difference of the camshaft with respect to the sprocket, the output shaft of the motor and the camshaft are linked by a speed change mechanism, and also includes a limit mechanism that moves the camshaft relative to The rotational phase difference of the sprocket is limited within the range of the required angle, and the sprocket is provided with a mounting cavity for the installation of the speed change mechanism.
  • the speed change mechanism includes an eccentric structure arranged on the output shaft of the motor and An eccentrically driven cycloidal disk and an output part linked with the cycloidal disk.
  • the two axial ends of the cycloidal disk are A and B respectively.
  • the A surface and the mounting cavity of the cycloidal disk are connected to the A surface.
  • a number of first ball fixing holes and enlarged holes distributed in the circumferential direction are arranged between the opposite opposing surfaces. The first ball fixing holes and the enlarged holes correspond one-to-one.
  • a cycloidal groove and a number of second ball fixing holes distributed around the circumference are arranged between the opposite faces of the faces, and between the first ball fixing hole and the enlarged hole, and between the second ball fixing hole and the cycloidal groove, respectively.
  • the speed change mechanism has only three parts.
  • the sprocket, the cycloidal disk and the output part are all driven by balls.
  • the parts are small, the installation is convenient, the overall size is thinner, and the diameter of the enlarged hole is larger than the ball diameter of the first ball.
  • the sprocket is equivalent to the housing of the speed change mechanism.
  • the input shaft drives the cycloidal disk to make an eccentric motion.
  • the sprocket is relatively stationary, the cycloidal disk swings relative to the sprocket.
  • the setting of the enlarged hole is to provide offset space for the cycloidal disk, so that the cycloidal disk can move in a cycloidal motion.
  • the bottom surface of the enlarged hole is an annular arc groove with a convex center, and the first ball can roll in the annular arc groove.
  • the bottom surface of the enlarged body can also be flat, preferably an annular arc groove, and the bottom of the annular arc groove is arc-shaped, which avoids the stress concentration phenomenon of the knife tip and strengthens the sprocket Or the strength of the cycloidal disk, and the ring-shaped arc grooves do not penetrate in the radial direction, which further strengthens the strength of the sprocket or the cycloidal disk, and the center of each ring-shaped arc groove surrounds a circle.
  • the vertical distance from the center of the first ball to the center line of the annular arc groove is equal to the eccentricity of the input shaft.
  • the distance between the center line of the circular arc groove and the center of the first ball is the eccentricity of the input shaft, and the first ball is in the circular arc groove It is a rolling fit, so that the friction is small, the noise is low, the use loss is low, the life is increased, the power consumption is low, and the driving power is saved.
  • the sprocket includes a sprocket body and an annular cover plate fixedly connected to the sprocket body, the first ball fixing hole or enlarged hole is provided on the inner wall of the sprocket body, and the annular cover plate is arranged on The output part realizes the axial limit cooperation with the output part.
  • the sprocket is composed of a sprocket body and an annular cover plate that are arranged in conjunction, and the sprocket body and the annular cover plate are connected by screws, which facilitates disassembly and assembly, and also facilitates the installation of the transmission mechanism.
  • the cylindrical part to which the spool fits the cylindrical part is horizontally Z-shaped, and its two ends correspond to the outer peripheral surface of the cycloidal disk and the outer peripheral surface of the input shaft respectively, and the middle part is opposite to the A surface of the cycloidal disk ,
  • the first ball fixing hole or enlarged hole is arranged on the inner wall of the middle part of the cylindrical part, the first bearing is arranged between the end of the cylindrical part corresponding to the input shaft and the input shaft, and the cycloid disc and the eccentric wheel of the input shaft There is a second bearing in between to reduce friction and reduce wear between components.
  • the limiting mechanism includes a first limiting block and a second limiting block respectively arranged on the annular cover and the output part, the first limiting block and the second limiting block are formed by rotating Limit the abutment and limit cooperation of the output part with respect to the rotational phase difference of the sprocket.
  • the opening and closing of the intake valve and exhaust valve have a certain range, so the camshaft cannot rotate at will. If the rotation range is too large, the structure of the intake valve and exhaust valve may be damaged. If it is too small, it may not be able to fully open.
  • the setting of the intake valve and exhaust valve, the first limit block and the second limit block can avoid the extreme cooperation between components and prolong the service life.
  • the first limiting block is provided on the inner peripheral surface of the annular cover plate, and the number is at least two, and the second limiting block is provided on the side of the output part facing the camshaft, and the number is There is at least one, and the second limiting block is located between the two first limiting blocks.
  • the movement process of the second limit block from abutting one of the first limit blocks to abutting the other first limit block is the movement stroke of the second limit block.
  • the second limit block rotates with the output part, so the rotatable angle of the second limit block is the range of the rotation phase difference between the output part and the sprocket.
  • the preferred first limit block and the second limit block The quantity can be the same and distributed evenly. There is a second limit block between every two adjacent first limit blocks, so that the resistance caused by the first limit block and the second limit block abutting is evenly distributed , And the resistance is large, the limit effect is better.
  • the first limiting block is provided on the inner peripheral surface of the annular cover plate, and the number is at least one, and the second limiting block is provided on the side of the output part facing the camshaft, and the number is at least There are two, and the first limiting block is located between the two second limiting blocks.
  • the movement of one of the second limit blocks and the first limit block abuts against the other first limit block and the first limit block is the movement of the second limit block Stroke
  • the rotatable angle of the second limit block is the range of the rotational phase difference between the output part and the sprocket.
  • the preferred first limit block and the second limit block The number of limit blocks can be the same and is evenly distributed. There is a first limit block between every two adjacent second limit blocks, so that the first limit block and the second limit block abut The resistance is evenly distributed, and the resistance is large, and the limit effect is better.
  • Figure 1 is a cross-sectional view of the overall structure of a specific embodiment of the present invention.
  • Figure 2 is a cross-sectional view of the overall structure of a specific embodiment of the present invention.
  • Fig. 3 is a schematic diagram of side A of the cycloid disc in the specific embodiment of the present invention.
  • Fig. 4 is a schematic diagram of the side B of the cycloid plate of the specific embodiment of the present invention.
  • Figure 5 is a cross-sectional view of the structure of the sprocket and the output part of the specific embodiment of the present invention.
  • Figure 6 is a cross-sectional view of the structure of the cycloid disk according to a specific embodiment of the present invention.
  • Fig. 7 is a partial enlarged view of a specific embodiment of the present invention.
  • Figure 8 is a perspective view of the structure of a specific embodiment of the invention.
  • Figure 9 is a cross-sectional view of the prior art structure
  • Fig. 10 is a cross-sectional view taken along the line D-D of Fig. 9.
  • a variable valve timing device with a vector cycloid transmission mechanism including a camshaft 1 that drives the intake valve or exhaust valve of the engine, and the same as the camshaft 1.
  • the shaft-rotating sprocket 2 and the motor 3 that changes the rotational phase difference of the camshaft 1 with respect to the sprocket 2, the output shaft 31 of the motor 3 and the camshaft 1 are linked by the transmission mechanism 4, and also include a limit mechanism 5.
  • the limit mechanism 5 limits the rotational phase difference of the camshaft 1 relative to the sprocket 2 within a required angle range.
  • the sprocket 2 is provided with an installation cavity 21 for the transmission mechanism 4 to be installed, so
  • the speed change mechanism 4 includes an eccentric structure arranged on the output shaft 31 of the motor 3, a cycloidal disk 42 eccentrically driven by the eccentric structure, and an output portion 43 linked with the cycloidal disk 42.
  • the output shaft 31 and the input shaft 41 of the motor 3 For the key connection, the rotation direction of the input shaft 41 can be forward or reverse, and its rotation speed is equal to or higher than the rotation speed of the sprocket 2.
  • the eccentric structure includes an input shaft 41 connected to the output shaft 31 of the motor 3 and an input shaft 41.
  • the upper eccentric wheel 411, the eccentric wheel 411 is used to drive the cycloidal disk 42 to perform eccentric movement.
  • the axial A surface 421 of the cycloidal disk 42 is provided with several enlarged holes 423 distributed around the circumference.
  • the mounting cavity 21 The opposite surface 211 opposite to the A surface 421 is provided with a number of first ball fixing holes 212 distributed around the circumferential direction.
  • the first ball fixing holes 212 and the enlarged holes 423 correspond one-to-one, of course, it can also be the shaft of the cycloid plate 42.
  • a surface 421 is provided with a plurality of first ball fixing holes 212 distributed in the circumferential direction, and the opposite surface 211 of the mounting cavity 21 opposite to the A surface 421 is provided with a plurality of enlarged holes 423 distributed in the circumferential direction.
  • a cycloidal groove 424 is provided on the axial B surface 422 of the cycloid disk 42, and a plurality of second ball fixing holes 432 distributed around the circumference are provided on the opposite surface 431 of the output portion 43 opposite to the B surface 422, of course.
  • the axial B surface 422 of the cycloid disk 42 is provided with a number of second ball fixing holes 432 distributed around the circumference, and the output portion 43 is provided with a cycloid groove 424 on the opposite surface 431 opposite to the B surface 422, Between the first ball fixing hole 212 and the enlarged hole 423, and between the second ball fixing hole 432 and the cycloid groove 424, a first ball 44 and a second ball 45 are respectively provided to make the cycloid disk 42 perform cycloid motion, and output The part 43 is linked to the camshaft 1.
  • the speed change mechanism 4 has only three parts.
  • the sprocket 2, the cycloidal disc 42 and the output part 43 are all driven by balls.
  • the sprocket 2 is equivalent to the housing of the speed change mechanism 4.
  • the input shaft 41 drives the cycloid plate 42 to make an eccentric motion.
  • the cycloid plate 42 oscillates relative to the sprocket 2, and the expansion hole 423 is provided to provide an offset space for the cycloid plate 42 so that the cycloid plate 42 can move in a cycloidal motion.
  • the outer peripheral surface of the cycloid plate 42 and the installation cavity There is a gap between the inner walls of 21 to prevent the cycloid plate 42 from colliding with the inner wall of the mounting cavity 21 during the cycloidal motion.
  • the output part 43 and the camshaft 1 are connected by a key, and the layout is reasonable.
  • the bottom surface of the enlarged hole 423 is a circular arc groove 4232 with a convex center 4231.
  • the height of the protrusion in the center 4231 is very small.
  • the end surface can be flat or pointed.
  • the inner wall of the circular arc groove 4232 and the first ball 44 Fitting together, the first ball 44 can roll in the annular arc groove 4232.
  • the bottom of the ring-shaped arc groove is arc-shaped, which avoids the point-like stress concentration phenomenon, strengthens the strength of the sprocket 2 or the cycloid plate 42, and the ring-shaped arc groove does not penetrate in the radial direction, which is further strengthened
  • the center of each annular arc groove 4232 is enclosed in a circle.
  • the vertical distance from the center of the first ball 44 to the center line of the annular arc groove 4232 is equal to the eccentricity r of the input shaft 41.
  • the distance between the center line of the circular arc groove 4232 and the center of the first ball 44 is the eccentricity of the input shaft 41.
  • the first ball 44 and the circular arc groove 4232 is a rolling fit, which makes friction, noise, low use loss, longer life, less power consumption, and saves driving power.
  • the above-mentioned sprocket 2 includes a sprocket body 22 and an annular cover plate 23 fixedly connected to the sprocket body 22.
  • the first ball fixing hole 212 or the enlarged hole 423 is provided on the inner wall of the sprocket body 22, and the annular cover plate 23 is arranged on The output part 43 realizes the axial limit cooperation with the output part 43.
  • the sprocket 2 is composed of a sprocket body 22 and an annular cover plate that are arranged in conjunction.
  • the sprocket body 22 and the annular cover plate 23 are connected by screws 24, which facilitates disassembly and assembly, and also facilitates the installation of the transmission mechanism 4.
  • the installation cavity 21 is located on the sprocket In the main body 22, the installation cavity 21 is formed by two coaxially arranged first cylindrical cavity 221 and second cylindrical cavity 222 connected by each other.
  • the diameters of the first cylindrical cavity 221 and the second cylindrical cavity 222 are different, so
  • the connection between the first cylindrical cavity 221 and the second cylindrical cavity 222 forms an annular connecting surface 223.
  • the annular connecting surface 223 is arranged opposite to the A surface 421 of the cycloid disk 42.
  • the mounting cavity 21 is opposite to the A surface of the cycloid disk 42.
  • the opposite surface 211 opposite to each other is the annular connecting surface 223.
  • the first ball fixing hole 212 or the enlarged hole 423 is provided on the annular connecting surface 223.
  • a first bearing is arranged between the inner wall of the first cylindrical cavity 221 and the input shaft 41.
  • a second bearing 02 is provided between the cycloidal disk 42 and the eccentric 411 of the input shaft 41, and a third bearing 03 is provided between the output part 43 and the input shaft 41.
  • the first bearing 01 and the second bearing 02 are both
  • the third bearing 03 is composed of a number of rollers which are sequentially surrounded into a ring to reduce friction and wear between components.
  • the cycloid disk 42 and the output part 43 are located in the second cylindrical cavity 222.
  • the above-mentioned limiting mechanism 5 includes a first limiting block 231 and a second limiting block 433 respectively arranged on the annular cover 23 and the output portion 43, the first limiting block 231 and the second limiting block
  • the rotation of the block 433 constitutes an abutment and limit cooperation that limits the rotational phase difference of the output portion 43 with respect to the sprocket 2. Since the opening and closing of the intake valve and exhaust valve have a certain range, the camshaft 1 cannot be rotated at will. If the rotation range is too large, the structure of the intake valve and exhaust valve may be damaged. If it is too small, the intake valve and exhaust valve may not be fully opened. For the exhaust valve, the arrangement of the first limit block 231 and the second limit block 433 can avoid the extreme cooperation between components and prolong the service life.
  • the first limiting block 231 is arranged on the inner peripheral surface of the annular cover 23, and the number is at least two, and the second limiting block 433 is arranged on the side of the output part 43 facing the camshaft 1.
  • the number is at least one.
  • the second limiting block 433 is located between the two first limiting blocks 231.
  • the movement process of the second limit block 433 from abutting one of the first limit blocks 231 to abutting the other first limit block 231 is the movement stroke of the second limit block 433, because the second limit block 433
  • the limit block 433 rotates with the output part 43, so the rotatable angle of the center point of the second limit block 433 is the range of the rotational phase difference of the output part 43 relative to the sprocket 2.
  • the preferred first limit block 231 The number of the second limiting block 433 and the second limiting block 433 can be the same and evenly distributed. There is a second limiting block 433 between every two adjacent first limiting blocks 231, so that the first limiting block 231 and the second limiting block 231 The resistance generated by the contact of the limit block 433 is evenly distributed, and the resistance is large, and the limit effect is better.
  • the first limiting block 231 is arranged on the inner peripheral surface of the annular cover 23, and the number is at least one, and the second limiting block 433 is arranged on the side of the output part 43 facing the camshaft 1, and The number is at least two, and the first limiting block 231 is located between the two second limiting blocks 433.
  • One of the second limit blocks 433 and the first limit block 231 abuts against the other first limit block 231 and the first limit block 231 abuts this movement process is the movement of the second limit block 433 Since the second limit block 433 rotates with the output part 43, the pivotable angle of the center point of the second limit block 433 is the range of the rotational phase difference of the output part 43 relative to the sprocket 2.
  • the preferred first The number of the first limit block 231 and the second limit block 433 can be the same and are evenly distributed. There is a first limit block 231 between every two adjacent second limit blocks 433. The resistance generated by the abutment between the block 231 and the second limiting block 433 is evenly distributed, and the resistance is large, and the limiting effect is better.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

一种具有矢量摆线变速机构的可变气门正时装置，包括凸轮轴（1）、与凸轮轴（1）同轴转动的链轮（2）以及使凸轮轴相对于链轮的旋转相位差变化的电机（3），电机的输出轴与凸轮轴之间通过变速机构（4）联动，变速机构包括设置在电机的输出轴上的偏心结构、受偏心结构偏心驱动的摆线盘（42）以及与摆线盘联动的输出部（43），摆线盘的A面（421）和安装腔（21）之间设置有第一滚珠固定孔（212）和扩大孔（423），摆线盘的B面（422）和输出部之间设置有摆线槽（424）和第二滚珠固定孔（432），第一滚珠固定孔（212）和扩大孔（423）之间以及第二滚珠固定孔（432）和摆线槽（424）之间分别设置有第一滚珠（44）和第二滚珠（45）。该可变气门正时装置部件少，体积小，布局合理。

Description

具有矢量摆线变速机构的可变气门正时装置 技术领域
本发明涉及变更发动机的进气门、排气门的开闭正时技术领域。
 背景技术
目前，一直以来，与汽车的运转状况对应，用于向发动机供给成为燃料的混合气体的进气门、用于排出燃烧气体的排气门根据发动机的动作行程而进行开闭。为了提高发动机的燃料消耗率、抑制废气，公知有将这些气门的开闭正时设为可变，按照发动机的运转状况而变更的具有矢量摆线变速机构的可变气门正时装置。
作为该可变气门正时装置，例如，如图9、10所示，存在下述可变气 门正时装置：将驱动发动机的气门的凸轮轴41、与从发动机传递旋转且驱动凸轮轴41旋转的链轮42可相对旋转地配置在同轴上，将与凸轮轴 41配置在同轴上的电动马达43的输出轴44的旋转经由减速机构45与连杆机构46传递到凸轮轴41，使凸轮轴41相对于链轮42相对旋转，使两者的旋转相位差产生变化，从而变更气门的开闭正时。
所述减速机构45被设为，内齿轮47的齿的一部分与设置于与链轮 42一体化的壳体48的外齿轮49啮合，该内齿轮47以旋转自如的方式 被轴承支承于电动马达43的输出轴44的偏心轴部44a，由此在使输出 轴“相对于链轮42相对旋转时，内齿轮47绕偏心轴部44a进行旋转， 所述减速机构45将该内齿轮47的旋转传递到导板50，进而将导板50 的旋转经由由臂46a、46b构成的连杆机构46传递到与凸轮轴41一体 旋转的凸轮盘41a，使凸轮轴41相对于链轮42相对旋转。
通过该凸轮轴41相对于链轮42的相对旋转，能够变更凸轮轴41 相对于曲轴的旋转相位的旋转相位，从而变更发动机的进气门或排气门的开闭的正时。
上述所记载的电动式的可变气门正时装置，将电动马达43 的输出轴44的旋转传递到凸轮轴41的机构，形成组合减速机构45与 连杆机构46的复杂的结构，存在不能紧凑地设计装置的问题。
在2012年公布的CN102482955A中，链轮和凸轮轴之间是通过RV减速机来实现凸轮轴与链轮之间的旋转相位差。
综合目前已公开的技术方案，均存在部件较多，安装工序繁琐，体积大等问题。
 技术问题
为了克服现有技术的不足，本发明提供了一种部件少，体积小的具有矢量摆线变速机构的可变气门正时装置。
 技术解决方案
为了实现上述目的，本发明采用的技术方案是：一种具有矢量摆线变速机构的可变气门正时装置，包括驱动发动机的进气门或排气门的凸轮轴、与凸轮轴同轴转动的链轮以及使凸轮轴相对于链轮的旋转相位差变化的电机，电机的输出轴与凸轮轴之间通过变速机构联动，还包括限位机构，该限位机构将所述凸轮轴相对于所述链轮的旋转相位差限制在所需角度的范围内，所述链轮上设置有供变速机构安装的安装腔，所述变速机构包括设置在电机的输出轴上的偏心结构、受偏心结构偏心驱动的摆线盘以及与摆线盘联动的输出部，所述摆线盘的轴向两端面分别为A面和B面，所述摆线盘的A面和安装腔上与A面相对的相对面之间设置有绕周向分布的若干个第一滚珠固定孔和扩大孔，第一滚珠固定孔和扩大孔一一对应，所述摆线盘的B面和输出部上与B面相对的相对面之间设置有摆线槽和绕周向分布的若干个第二滚珠固定孔，第一滚珠固定孔和扩大孔之间以及第二滚珠固定孔和摆线槽之间分别设置有使摆线盘做摆线运动的第一滚珠和第二滚珠，输出部与凸轮轴联动连接。
 有益效果
上述技术方案中，变速机构只有三个部件，链轮、摆线盘和输出部之间均通过滚珠传动，部件少，安装方便，整体尺寸变薄，扩大孔的口径大于第一滚珠的球直径，链轮相当于变速机构的壳体，当电机的转速与链轮的转速不一致时，输入轴驱动摆线盘做偏心运动，因链轮是相对静止的，所以摆线盘相对于链轮摆动，扩大孔的设置就是为了给摆线盘提供偏移空间，使摆线盘能呈摆线运动，摆线盘的外侧周面与安装腔的内壁之间存在间隙，避免摆线盘在做摆线运动时碰撞到安装腔内壁，输出部与凸轮轴之间通过键连接，布局合理。
作为本发明的进一步设置，所述扩大孔的底面为中心凸起的环形圆弧槽，第一滚珠可在环形圆弧槽内滚动。
上述技术方案中，扩大体的底面也可以是平面状，优选的为环形圆弧槽，环状圆弧槽的底部是圆弧形的，避免了刀尖状的应力集中现象，加强了链轮或摆线盘的强度，且环状圆弧槽在径向不穿通，进一步加强了链轮或摆线盘的强度，各个环形圆弧槽的圆心围绕成一个圆。
作为本发明的进一步设置，所述第一滚珠的球心到环形圆弧槽的中心线的垂直距离等于输入轴的偏心量。
上述技术方案中，当第一滚珠位于环形圆弧槽内时，环形圆弧槽的中心线到第一滚珠球心之间的距离为输入轴的偏心量，第一滚珠与环形圆弧槽内是滚动配合，使得摩擦小，噪音小，使用损耗低，寿命增大，功率消耗少，节省驱动电能。
作为本发明的进一步设置，所述链轮包括链轮本体以及与链轮本体固定连接的环形盖板，第一滚珠固定孔或扩大孔设置在链轮本体的内壁上，环形盖板盖设在输出部上实现与输出部的轴向限位配合。
上述技术方案中，链轮由相合设置的链轮本体和环形盖板组成，链轮本体与环形盖板通过螺丝连接，这样方便拆装，也方便变速机构的安装，链轮本体上具有与摆线盘适配的圆筒部，圆筒部呈横放的Z字型，其两端分别与摆线盘的外周面和输入轴的外周面对应，中部与摆线盘的A面相对设置，第一滚珠固定孔或扩大孔设置在圆筒部的中部内壁上，圆筒部与输入轴对应的端部与输入轴之间设置有第一轴承，摆线盘与输入轴的偏心轮之间设有第二轴承，减少摩擦，减小部件之间的磨损。
作为本发明的进一步设置，所述限位机构包括分别设置在环形盖板和输出部上的第一限位块和第二限位块，第一限位块和第二限位块经转动构成限制输出部相对于链轮的旋转相位差的抵接限位配合。
上述技术方案中，因进气门和排气门的开合具有一定范围，所以凸轮轴不能随意转动，转动范围过大可能会损坏进气门和排气门的结构，过小可能无法完全打开进气门和排气门，第一限位块和第二限位块的设置可避免部件之间的极限配合，延长使用寿命。
作为本发明的进一步设置，所述第一限位块设置在环形盖板的内侧周面上，且数量至少为两个，第二限位块设置在输出部朝向凸轮轴的一侧，且数量至少为一个，所述第二限位块位于两第一限位块之间。
上述技术方案中，第二限位块从与其中一个第一限位块抵接到与另一个第一限位块抵接的这一运动过程即为第二限位块的运动行程，因第二限位块是随输出部转动的，所以第二限位块的可转动角度即为输出部相对于链轮的旋转相位差的范围，优选的第一限位块和第二限位块的数量可以一致，且呈均匀分布，每相邻两第一限位块之间均有一个第二限位块，这样由第一限位块和第二限位块抵接而产生的阻力分布均匀，且阻力大，限位效果更好。
作为本发明的进一步设置，所述第一限位块设置在环形盖板的内侧周面上，且数量至少为一个，第二限位块设置在输出部朝向凸轮轴的一侧，且数量至少为两个，所述第一限位块位于两第二限位块之间。
上述技术方案中，其中一个第二限位块与第一限位块抵接到另一个第一限位块与第一限位块抵接的这一运动过程即为第二限位块的运动行程，因第二限位块是随输出部转动的，所以第二限位块的可转动角度即为输出部相对于链轮的旋转相位差的范围，优选的第一限位块和第二限位块的数量可以一致，且呈均匀分布，每相邻两第二限位块之间均有一个第一限位块，这样由第一限位块和第二限位块抵接而产生的阻力分布均匀，且阻力大，限位效果更好。
下面结合附图对本发明作进一步描述。
 附图说明
附图1为本发明具体实施例整体结构剖视图；
附图2为本发明具体实施例整体结构剖视图；
附图3为本发明具体实施例摆线盘的A面示意图；
附图4为本发明具体实施例摆线盘的B面示意图；
附图5为本发明具体实施例链轮及输出部的结构剖视图；
附图6为本发明具体实施例摆线盘的结构剖视图；
附图7为本发明具体实施例局部放大图；
附图8为本发明具体实施例结构立体图；
附图9为现有技术的结构剖视图；
附图10为沿着附图9的D-D线的剖视图。
 本发明的最佳实施方式
在此处键入本发明的最佳实施方式描述段落。
 本发明的实施方式
本发明的具体实施例如图1-8所示，一种具有矢量摆线变速机构的可变气门正时装置，包括驱动发动机的进气门或排气门的凸轮轴1、与凸轮轴1同轴转动的链轮2以及使凸轮轴1相对于链轮2的旋转相位差变化的电机3，电机3的输出轴31与凸轮轴1之间通过变速机构4联动，还包括限位机构5，该限位机构5将所述凸轮轴1相对于所述链轮2的旋转相位差限制在所需角度的范围内，所述链轮2上设置有供变速机构4安装的安装腔21，所述变速机构4包括设置在电机3的输出轴31上的偏心结构、受偏心结构偏心驱动的摆线盘42以及与摆线盘42联动的输出部43，电机3的输出轴31与输入轴41为键连接，输入轴41的转动方向可正转或反转，其转动速度等于或高于链轮2的转动速度，偏心结构包括与电机3的输出轴31连接的输入轴41以及设置在输入轴41上的偏心轮411，偏心轮411用于驱动摆线盘42做偏心运动，所述摆线盘42的轴向A面421上设置有绕周向分布的若干个扩大孔423，安装腔21上与A面421相对的相对面211上设置有绕周向分布的若干个第一滚珠固定孔212，第一滚珠固定孔212和扩大孔423一一对应，当然也可以是摆线盘42的轴向A面421上设置有绕周向分布的若干个第一滚珠固定孔212，安装腔21上与A面421相对的相对面211上设置有绕周向分布的若干个扩大孔423，所述摆线盘42的轴向B面422上设置有摆线槽424，输出部43上与B面422相对的相对面431上设置有绕周向分布的若干个第二滚珠固定孔432，当然也可以是摆线盘42的轴向B面422上设置有绕周向分布的若干个第二滚珠固定孔432，输出部43上与B面422相对的相对面431上设置有摆线槽424，第一滚珠固定孔212和扩大孔423之间以及第二滚珠固定孔432和摆线槽424之间分别设置有使摆线盘42做摆线运动的第一滚珠44和第二滚珠45，输出部43与凸轮轴1联动连接。变速机构4只有三个部件，链轮2、摆线盘42和输出部43之间均通过滚珠传动，部件少，安装方便，整体尺寸变薄，扩大孔423的口径大于第一滚珠44的球直径，链轮2相当于变速机构4的壳体，当电机3的转速与链轮2的转速不一致时，输入轴41驱动摆线盘42做偏心运动，因链轮2是相对静止的，所以摆线盘42相对于链轮2摆动，扩大孔423的设置就是为了给摆线盘42提供偏移空间，使摆线盘42能呈摆线运动，摆线盘42的外侧周面与安装腔21的内壁之间存在间隙，避免摆线盘42在做摆线运动时碰撞到安装腔21内壁，输出部43与凸轮轴1之间通过键连接，布局合理。
上述扩大孔423的底面为中心4231凸起的环形圆弧槽4232，中心4231凸起的高度很小，其端面可以是平面状也可以是尖顶，环形圆弧槽4232的内壁与第一滚珠44贴合，第一滚珠44可在环形圆弧槽4232内滚动。环状圆弧槽的底部是圆弧形的，避免了刀尖状的应力集中现象，加强了链轮2或摆线盘42的强度，且环状圆弧槽在径向不穿通，进一步加强了链轮2或摆线盘42的强度，各个环形圆弧槽4232的圆心围绕成一个圆。
上述第一滚珠44的球心到环形圆弧槽4232的中心线的垂直距离等于输入轴41的偏心量r。当第一滚珠44位于环形圆弧槽4232内时，环形圆弧槽4232的中心线到第一滚珠44球心之间的距离为输入轴41的偏心量，第一滚珠44与环形圆弧槽4232内是滚动配合，使得摩擦小，噪音小，使用损耗低，寿命增大，功率消耗少，节省驱动电能。
上述链轮2包括链轮本体22以及与链轮本体22固定连接的环形盖板23，第一滚珠固定孔212或扩大孔423设置在链轮本体22的内壁上，环形盖板23盖设在输出部43上实现与输出部43的轴向限位配合。链轮2由相合设置的链轮本体22和环形盖板组成，链轮本体22与环形盖板23通过螺丝24连接，这样方便拆装，也方便变速机构4的安装，安装腔21位于链轮本体22内，安装腔21由两个同轴设置的第一圆柱形腔221和第二圆柱形腔222连通而成，第一圆柱形腔221和第二圆柱形腔222的直径不一样，所以第一圆柱形腔221和第二圆柱形腔222的连接处形成一个环形连接面223，环形连接面223与摆线盘42的A面421相对设置，安装腔21上与摆线盘42的A面相对的相对面211即为环形连接面223，第一滚珠固定孔212或扩大孔423设置在环形连接面223上，第一圆柱形腔221的内壁与输入轴41之间设置有第一轴承01，摆线盘42与输入轴41的偏心轮411之间设有第二轴承02，输出部43与输入轴41之间设置有第三轴承03，第一轴承01和第二轴承02均为滚珠轴承，第三轴承03由若干个滚柱依次围绕成环构成，减少摩擦，减小部件之间的磨损，摆线盘42和输出部43位于第二圆柱形腔222内。
如图8所示，上述限位机构5包括分别设置在环形盖板23和输出部43上的第一限位块231和第二限位块433，第一限位块231和第二限位块433经转动构成限制输出部43相对于链轮2的旋转相位差的抵接限位配合。因进气门和排气门的开合具有一定范围，所以凸轮轴1不能随意转动，转动范围过大可能会损坏进气门和排气门的结构，过小可能无法完全打开进气门和排气门，第一限位块231和第二限位块433的设置可避免部件之间的极限配合，延长使用寿命。
实施例一，所述第一限位块231设置在环形盖板23的内侧周面上，且数量至少为两个，第二限位块433设置在输出部43朝向凸轮轴1的一侧，且数量至少为一个，所述第二限位块433位于两第一限位块231之间。第二限位块433从与其中一个第一限位块231抵接到与另一个第一限位块231抵接的这一运动过程即为第二限位块433的运动行程，因第二限位块433是随输出部43转动的，所以第二限位块433中心点的可转动角度即为输出部43相对于链轮2的旋转相位差的范围，优选的第一限位块231和第二限位块433的数量可以一致，且呈均匀分布，每相邻两第一限位块231之间均有一个第二限位块433，这样由第一限位块231和第二限位块433抵接而产生的阻力分布均匀，且阻力大，限位效果更好。
实施例二，所述第一限位块231设置在环形盖板23的内侧周面上，且数量至少为一个，第二限位块433设置在输出部43朝向凸轮轴1的一侧，且数量至少为两个，所述第一限位块231位于两第二限位块433之间。其中一个第二限位块433与第一限位块231抵接到另一个第一限位块231与第一限位块231抵接的这一运动过程即为第二限位块433的运动行程，因第二限位块433是随输出部43转动的，所以第二限位块433中心点的可转动角度即为输出部43相对于链轮2的旋转相位差的范围，优选的第一限位块231和第二限位块433的数量可以一致，且呈均匀分布，每相邻两第二限位块433之间均有一个第一限位块231，这样由第一限位块231和第二限位块433抵接而产生的阻力分布均匀，且阻力大，限位效果更好。
本发明不局限于上述具体实施方式，本领域一般技术人员根据本发明公开的内容，可以采用其他多种具体实施方式实施本发明的，或者凡是采用本发明的设计结构和思路，做简单变化或更改的，都落入本发明的保护范围。

Claims (7)

  1. 一种具有矢量摆线变速机构的可变气门正时装置，包括驱动发动机的进气门或排气门的凸轮轴、与凸轮轴同轴转动的链轮以及使凸轮轴相对于链轮的旋转相位差变化的电机，电机的输出轴与凸轮轴之间通过变速机构联动，还包括限位机构，该限位机构将所述凸轮轴相对于所述链轮的旋转相位差限制在所需角度的范围内，其特征在于：所述链轮上设置有供变速机构安装的安装腔，所述变速机构包括设置在电机的输出轴上的偏心结构、受偏心结构偏心驱动的摆线盘以及与摆线盘联动的输出部，所述摆线盘的轴向两端面分别为A面和B面，所述摆线盘的A面和安装腔上与A面相对的相对面之间设置有绕周向分布的若干个第一滚珠固定孔和扩大孔，第一滚珠固定孔和扩大孔一一对应，所述摆线盘的B面和输出部上与B面相对的相对面之间设置有摆线槽和绕周向分布的若干个第二滚珠固定孔，第一滚珠固定孔和扩大孔之间以及第二滚珠固定孔和摆线槽之间分别设置有使摆线盘做摆线运动的第一滚珠和第二滚珠，输出部与凸轮轴联动连接。
  2. 根据权利要求1所述的具有矢量摆线变速机构的可变气门正时装置，其特征在于：所述扩大孔的底面为中心凸起的环形圆弧槽，第一滚珠可在环形圆弧槽内滚动。
  3. 根据权利要求2所述的具有矢量摆线变速机构的可变气门正时装置，其特征在于：所述第一滚珠的球心到环形圆弧槽的中心线的垂直距离等于输入轴的偏心量。
  4. 根据权利要求1或2或3所述的具有矢量摆线变速机构的可变气门正时装置，其特征在于：所述链轮包括链轮本体以及与链轮本体固定连接的环形盖板，第一滚珠固定孔或扩大孔设置在链轮本体的内壁上，环形盖板盖设在输出部上实现与输出部的轴向限位配合。
  5. 根据权利要求4所述的具有矢量摆线变速机构的可变气门正时装置，其特征在于：所述限位机构包括分别设置在环形盖板和输出部上的第一限位块和第二限位块，第一限位块和第二限位块经转动构成限制输出部相对于链轮的旋转相位差的抵接限位配合。
  6. 根据权利要求5所述的具有矢量摆线变速机构的可变气门正时装置，其特征在于：所述第一限位块设置在环形盖板的内侧周面上，且数量至少为两个，第二限位块设置在输出部朝向凸轮轴的一侧，且数量至少为一个，所述第二限位块位于两第一限位块之间。
  7. 根据权利要求5所述的具有矢量摆线变速机构的可变气门正时装置，其特征在于：所述第一限位块设置在环形盖板的内侧周面上，且数量至少为一个，第二限位块设置在输出部朝向凸轮轴的一侧，且数量至少为两个，所述第一限位块位于两第二限位块之间。
PCT/CN2019/098610 2019-06-18 2019-07-31 具有矢量摆线变速机构的可变气门正时装置 WO2020252854A1 (zh)

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